Valve device, pressure and / or flow control valve and method for operating the pressure and / or flow control valve

Abstract

The invention relates to a valve device (80a-d), in particular a pressure and / or quantity control valve device, preferably for hydrogen gas and / or hydrogen-containing gas mixtures, with a nozzle assembly (10a-d) which forms at least one flow channel (12a-d) and a valve seat (16a-d) surrounding a flow channel opening (14a-d) of the flow channel (12a-d), and with a valve tappet unit (18a-d) which forms a sealing contour, preferably circumferential, at an axial end (20a-d) which is provided for a seat on the valve seat (16a-d) which selectively closes the flow channel (12a-d) gas-tight, in particular hydrogen gas-tight. It is proposed that the nozzle assembly (10a-d) has at least in a region radially outside the valve seat (16a-d) and facing the valve tappet assembly (18a-d) a geometric flow optimization unit (22a-d) with at least one flow shaping geometry (24a-d).

Description

State of the art

[0001] The invention relates to a valve device according to the preamble of claim 1, a pressure and / or quantity control valve according to the preamble of claim 24 and a method according to the preamble of claim 25.

[0002] A valve assembly for a pressure and / or flow control valve has already been proposed, comprising a nozzle assembly that forms at least one flow channel and a valve seat surrounding a flow channel opening, and a valve tappet assembly that forms a sealing contour, preferably circumferential, at one axial end, which is designed to selectively seal the flow channel gas-tight, particularly hydrogen gas-tight, on the valve seat. Pressure and / or flow control valves generally require flow-current and flow-force characteristics that are as linear as possible. In the prior art, this is achieved by a control geometry on a conical seat geometry of a valve tappet assembly. This can lead to manufacturing limitations. Furthermore, a conical seat may be unsuitable for meeting high tightness requirements for the valve assembly.Flat seats generally offer a higher degree of tightness, but lead to non-linear mass flows and non-linear flow force profiles over the stroke, which can significantly reduce the control quality.

[0003] The object of the invention is, in particular, to provide a generic device with advantageous properties regarding the linearity of flow (mass flow)-current and flow-force (flow force) characteristics while simultaneously maintaining high tightness. This object is achieved according to the invention by the features of claims 1, 24, and 25, while advantageous embodiments and further developments of the invention can be found in the dependent claims. Advantages of the invention

[0004] The invention relates to a valve device, in particular a pressure and / or quantity control valve device, preferably for hydrogen gas and / or hydrogen-containing gas mixtures, with a nozzle assembly which forms at least one flow channel and a valve seat surrounding a flow channel opening of the flow channel, and with a valve tappet unit which forms a sealing contour, preferably circumferential, at an axial end, which is provided for a selectively gas-tight, in particular hydrogen gas-tight, fit on the valve seat.

[0005] It is proposed that the nozzle assembly, at least in a region radially outer relative to the valve seat and facing the valve tappet assembly, incorporates a geometric flow optimization unit with at least one flow-shaping geometry. This allows for advantageous characteristic curves to be achieved, particularly independent of the design and / or valve seat type of the valve tappet assembly. Advantageously, a high degree of sealing can be achieved while simultaneously maintaining good, and especially linear, controllability.

[0006] In particular, the valve device, preferably the pressure and / or flow control valve, and more preferably the pressure-opening (proportional) pressure and / or flow control valve for gases, is designed to influence a gas flow that at least contains hydrogen gas or is at least predominantly composed of hydrogen gas. Alternatively, the valve device, preferably the pressure and / or flow control valve, and more preferably the pressure-opening (proportional) pressure and / or flow control valve for gases, can also be designed to influence other gas flows, such as nitrogen, oxygen, carbon dioxide, natural gas, LPG, etc. "Designed" is understood to mean specifically programmed, designed, and / or equipped.The phrase "an object is intended for a specific function" means, in particular, that the object fulfills and / or performs this specific function in at least one application and / or operating condition. In particular, the valve device is especially well-suited for pressure-opening (proportional) pressure and / or flow control valves for gases, in which a spring force closes the valve stem unit against an inlet pressure of the gas and in which a magnetic force from an electromagnet driving the valve stem unit points in the direction of action of the inlet pressure of the gas.

[0007] The valve tappet assembly forms, in particular, at least one valve tappet of the pressure and / or flow control valve. The valve tappet assembly can be designed as a single piece or in multiple parts. It is conceivable that the valve tappet assembly interacts with a separate valve armature, in particular a magnetic armature, which drives the valve tappet assembly. However, it is also conceivable that the valve tappet assembly integrally comprises a valve armature, in particular the magnetic armature. In particular, the valve tappet assembly is designed to transmit a setting of the pressure and / or flow control valve into a function of the pressure and / or flow control valve, e.g., a position of a sealing element or the sealing contour of the pressure and / or flow control valve. The valve tappet assembly is movably mounted in the pressure and / or flow control valve, in particular along an axial direction.In particular, the axial position of the valve tappet unit determines the gas flow through the pressure and / or flow control valve. The pressure and / or flow control valve may, for example, include an electromagnet to generate the actuating movement and / or to adjust the position of the valve tappet unit. The current required for a specific tappet unit setting determines the mass flow-stroke and / or force-stroke characteristics of the pressure and / or flow control valve, and thus also the flow-current characteristic. By adjusting the axial position of the valve tappet unit, the sealing contour is either placed on or lifted from the valve seat.

[0008] The axial end of the valve tappet assembly preferably closes the valve tappet assembly on a side facing the axial direction (or away from the axial direction). The valve tappet assembly preferably includes a sealing element. The sealing element is designed, in particular, to seal a nozzle of the nozzle assembly, especially the pressure and / or flow control valve, preferably in a gas-tight, and preferably hydrogen-gas-tight manner. The sealing element comprises the sealing contour of the valve tappet assembly. The sealing contour is preferably a closed sealing contour. The sealing contour preferably overlaps with an opening contour of the nozzle. The opening contour of the nozzle is formed, in particular, by the flow channel opening of the flow channel. The flow channel opening of the flow channel of the nozzle assembly is limited on a side facing the valve tappet assembly by the opening contour of the nozzle.To close the nozzle, the sealing element with its sealing contour contacts the opening contour of the nozzle. The nozzle assembly, particularly of the pressure and / or flow control valve, preferably includes the valve seat. The valve seat is, in particular, a part of the nozzle assembly, especially the nozzle itself. The valve seat preferably includes the opening contour of the nozzle.

[0009] The geometric flow optimization unit is designed and / or arranged separately from the valve tappet unit. Radial directions run in a plane perpendicular to the axial direction. The geometric flow optimization unit lies outside the valve seat, particularly the nozzle opening contour, in the radial direction(s). The flow-shaping geometry is preferably oriented towards the valve tappet unit and, in particular, towards a flow space between the nozzle assembly and the valve tappet unit. Preferably, the flow-shaping geometry at least partially delimits the flow space, preferably at least on one (axial) side. The flow space particularly forms an interior space of the valve. The flow space preferably lies, at least partially, in the axial direction between the valve tappet unit and the nozzle assembly.The flow chamber is preferably located, at least in part, radially between the valve tappet assembly and the nozzle assembly. Depending on the position of the valve tappet assembly, the flow chamber is either permeable or sealed. The geometric flow optimization unit is specifically designed to influence / guide the gas flow exiting the flow channel when the pressure and / or flow control valve is open. The geometric flow optimization unit comprises at least one surface element specifically designed to influence the flow. Specifically, the geometric flow optimization unit comprises at least one surface element whose surface normal is angled to the axial direction of the valve tappet assembly and preferably to a perpendicular to the surface normal.In particular, the geometric flow optimization unit comprises at least one surface region inclined to the axial direction, which can come into contact with the flowing gas. Specifically, a single, at least substantially rectangular step or a plurality of at least substantially rectangular steps does not constitute a flow optimization unit within the meaning of this disclosure. In particular, the geometric flow optimization unit is rotationally symmetrical about a central axis of the flow channel, the valve tappet assembly, and / or the valve seat. In particular, the geometric flow optimization unit surrounds the sealing element of the valve tappet assembly, at least in a closed state of the pressure and / or flow control valve, in an approximately semi-shell-like manner.

[0010] Furthermore, it is proposed that the geometric flow optimization unit be designed to linearize at least one valve characteristic curve, in particular a flow-current characteristic curve and / or flow-force characteristic curve of a valve comprising the valve tappet unit. Advantageously, high tightness can be achieved while maintaining good and linear controllability.

[0011] Furthermore, it is proposed that the flow-shaping geometry be designed as a conical recess, preferably centered around a central axis of the flow channel, which tapers in the closing direction of the valve tappet assembly. This allows advantageous characteristic curves to be achieved, particularly regardless of the design and / or valve seat type of the valve tappet assembly. The central axis preferably runs centrally through the flow channel, particularly at least in the immediate vicinity of the flow channel opening. The closing direction preferably runs at least substantially parallel to the central axis of the flow channel. The closing direction is preferably directed towards the valve seat and / or away from the valve tappet assembly. The conical recess is particularly a depression or milled area having a conical shape.Since the conical recess is located outside the valve tappet assembly and outside the flow channel of the nozzle assembly, it is preferably also called an external conical recess. In particular, the nozzle opening contour and the flow channel itself are free of any flow-optimizing geometry. Specifically, the conical recess completely surrounds the valve seat. Specifically, the conical recess completely surrounds a portion of the flow channel. Specifically, the conical recess completely surrounds the nozzle opening contour. Specifically, the conical recess completely surrounds a portion of the valve tappet assembly, at least when the valve is closed. In particular, a central axis of the conical recess runs parallel to the central axis of the flow channel. Preferably, the central axis of the conical recess overlaps with the central axis of the flow channel. Preferably, the conical recess is rotationally symmetrical.

[0012] If the valve tappet assembly is partially immersed in the conical recess, at least in one operating state where it rests on the valve seat, and preferably in all regular operating states, an advantageous influence on the flow-stroke and force-stroke characteristics can be achieved. Advantageously, optimized flow guidance between the valve tappet assembly and the conical recess can be achieved. In particular, an axial end of the valve tappet assembly, which includes the sealing element, immerses in the conical recess. The conical recess preferably forms a completely enclosed space, which is at least partially filled by an object when it is immersed in it. In particular, the inner diameter of the conical recess is significantly larger than the outer diameter of the valve tappet assembly, especially that of the axial end of the valve tappet assembly, over a predominant portion of the recess.In particular, the conical recess is designed to prevent flow reversals. This advantageously avoids undefined operating points of a valve with the valve assembly.

[0013] If at least a large portion, preferably an entire side wall, of the conical recess is free of curvature in the axial direction of the conical recess, simple and / or precise manufacturing can be advantageously achieved. Furthermore, this allows for advantageous flow guidance. In particular, the conical recess forms a straight cone. "Large portion" is understood to mean, in particular, 51%, preferably 66%, preferably 75%, and most preferably 90%. The axial direction preferably overlaps the central axis of the conical recess.

[0014] In this context, it is proposed that at least a large portion of a side wall of the conical recess has a cone angle between 10° and 80°, preferably between 20° and 70°, and more preferably between 30° and 60°. This allows for advantageous / optimal flow guidance. A cone angle of approximately 45° is particularly preferred. The cone angle is preferably an angle formed by a side wall of the conical recess relative to the central axis / axial direction of the conical recess.

[0015] Furthermore, it is proposed that an entire slope region of the conical recess be located radially further outward than the axial end of the valve tappet assembly. This would allow for advantageous flow characteristics, particularly flow linearization properties. Alternatively, however, it is also conceivable that the slope region of the conical recess could project inward beyond the radial position of the valve tappet assembly. This would mean that part of the slope region of the conical recess would be located radially further inward than the axial end of the valve tappet assembly.

[0016] If, as an alternative to the aforementioned design, at least part of a side wall of the cone recess is curved concavely or convexly in the axial direction of the cone recess, an advantageous influence on the flow-stroke and force-stroke characteristics can be achieved, especially with a simultaneously compact design of the valve device.

[0017] Additionally, it is proposed that the geometric flow optimization unit incorporates one or more further flow shaping geometries, which differ, in particular, from a cone geometry. This allows for a particularly precise adjustment of the valve's characteristic curves. Furthermore, it advantageously optimizes the flow through the valve.

[0018] The additional flow-shaping geometry(s) are preferably arranged spatially separated from the flow-shaping geometry. The additional flow-shaping geometry(s) are preferably non-overlapping with the flow-shaping geometry. The additional flow-shaping geometry(s) can be arranged radially within the cone recess and / or radially outside the cone recess. The additional flow-shaping geometry(s) can be arranged axially above the cone recess and / or axially below the cone recess. Alternatively, however, it is also conceivable that the cone recess has an interruption in the radial and / or axial direction within which the additional flow-shaping geometry is arranged.Preferably, the conical recess is continuous / uninterrupted. In particular, the flow-shaping geometry and / or the further flow-shaping geometry(ies) are formed by the same component of the nozzle assembly.

[0019] If the further flow shaping geometry, or at least one of the several further flow shaping geometries, is arranged radially between the flow channel opening and the flow shaping geometry, an advantageous flow control, in particular a linearization of the characteristic curves, can be achieved.

[0020] If the further flow-shaping geometry, or at least one of the several further flow-shaping geometries, in particular the further flow-shaping geometry arranged radially between the flow channel opening and the flow-shaping geometry, is designed as a flow edge, it is advantageously possible to prevent flow from contacting the nozzle contour. Advantageously, a transition from a flow contacting the valve tappet assembly to a flow contacting the cone recess can be forced. Advantageously, especially with larger strokes, a change in the flow direction towards the valve tappet assembly can be avoided. This advantageously prevents undefined operating points of a valve with the valve assembly. The flow edge can have a stepped cross-section, in particular with a 90° angle, or an angle deviating from 90°, e.g.The flow edge(s) are located between 60° and 120°, between 70° and 110°, or between 80° and 100°. The flow edge(s) is / are arranged within a radial region of the nozzle assembly / flow optimization unit, which overlaps with a radial region of the valve tappet assembly. Here, "radial region" is understood to mean, in particular, a region extending radially from a central axis over which an object extends.

[0021] It is proposed that the flow edge, or at least one of the flow edges, forms a flow separation edge for a gas flow exiting the flow channel opening in the direction of the flow-shaping geometry. This advantageously prevents the flow from adhering to the nozzle contour. Advantageously, characteristic curve linearization can be achieved. The flow separation edge is preferably located below the valve tappet assembly. The flow separation edge is preferably located behind / below the valve tappet assembly when viewed in the closing direction. The flow separation edge preferably forms a step extending away from the valve tappet assembly along a radial direction emanating from a center point.The flow separation edge, viewed along a radial direction emanating from a central axis of the valve tappet unit or the cone recess, forms a descending step.

[0022] Alternatively or additionally, it is proposed that the flow edge, or at least one of the flow edges, forms a guide edge for a gas flow radially into the flow-shaping geometry. This advantageously prevents the flow from adhering to the nozzle contour. Characteristic curve linearization can also be advantageously achieved. In particular, the further flow-shaping geometry is a separation edge, and an additional further flow-shaping geometry is the guide edge. Preferably, the flow optimization unit has the separation edge and the guide edge. Preferably, the separation edge and the guide edge are designed differently from each other and / or arranged spatially separately. The guide edge is preferably arranged below the valve tappet unit. Viewed in the closing direction of the valve tappet unit, the guide edge is preferably arranged behind / below the valve tappet unit.The guide edge preferably forms a step approaching the valve tappet assembly when viewed along a radial direction radiating from a center point. Viewed along a radial direction radiating from a central axis of the valve tappet assembly or the conical recess, the guide edge forms a rising step. A radially extending (parallel to the radial direction) flat area is preferably arranged between the flow separation edge and the guide edge. The guide edge is particularly positioned between the flow separation edge and the conical recess.

[0023] Alternatively or additionally, it is proposed that the further flow-shaping geometry, or at least one of the several further flow-shaping geometries, be arranged radially further outwards than the flow-shaping geometry. This allows for advantageous flow control, particularly linearization of the characteristic curves.

[0024] If the further flow-shaping geometry, or at least one of the several further flow-shaping geometries, is designed as an axial flow deflection, the flow can advantageously be guided axially along the valve tappet unit on the outlet side. Advantageously, characteristic curve linearization can be achieved. The axial flow deflection is specifically intended to redirect the flow exiting the cone recess in the axial direction. "Specified" is to be understood as being specifically programmed, designed, and / or equipped. The fact that an object is intended for a specific function is to be understood as meaning that the object fulfills and / or performs this specific function in at least one application and / or operating condition. The axial flow deflection can be formed by a cylindrical section of the geometric flow optimization unit.The axial flow deflection can be formed by wall regions of the nozzle assembly extending parallel to the axial direction. Alternatively, the axial flow deflection can be formed by wall regions of the nozzle assembly extending at an angle to the axial direction, the angle of which to the axial direction is significantly smaller than the cone angle of the conical recess. In particular, the angle of the axial flow deflection to the axial direction is at least 5°, preferably at least 10°, more preferably at least 20°, and most preferably at least 30° smaller than the cone angle of the conical recess.

[0025] Furthermore, it is proposed that the axial flow deflection is designed to generate a flow direction for the gas flow exiting the flow optimization unit after passing through all flow-shaping geometries of the flow optimization unit. This direction's angle to an axial direction of the valve tappet unit is significantly smaller than the cone angle, or it runs at least substantially parallel to the axial direction of the valve tappet unit. This advantageously allows the flow to be guided axially along the outlet side of the valve tappet unit. Advantageously, characteristic curve linearization can be achieved. In particular, the angle of the gas flow to the axial direction of the valve tappet unit is at least 5°, preferably at least 10°, more preferably at least 20°, and most preferably at least 30° smaller than the cone angle of the cone recess.The flow direction after passing through all flow-shaping geometries of the flow optimization unit can run at least essentially perpendicular to an outlet channel of a gas outlet of the valve device.

[0026] Furthermore, it is proposed that the geometric flow optimization unit, extending radially from the inside (central axis) to the outside (gas outlet), particularly in the flow direction, comprises the following sequence of flow-shaping geometries: i) the flow separation edge, ii) a horizontally planar flow region, iii) the guide edge, iv) the conical recess, and v) the axial flow deflection. This advantageously allows for characteristic curve linearization.

[0027] Furthermore, it is proposed that the nozzle assembly comprises a monolithic component which simultaneously forms the flow channel and the flow-shaping geometry of the geometric flow optimization unit, preferably the entire flow optimization unit. This advantageously allows for high compactness, tightness, and / or stability. In addition, complexity can be advantageously kept low. Simple assembly is also advantageously achieved. The nozzle assembly can, in particular, be formed entirely by the monolithic component, or the monolithic component can be one of several sub-components of the nozzle assembly that are connected, at least during assembly. In this embodiment, the geometric flow optimization unit is integrated with the nozzle.

[0028] Alternatively, it is proposed that the flow channel and the flow-shaping geometry are each formed by separate components of the nozzle assembly, which are mounted together, particularly at least during assembly. This advantageously enables simple manufacturing, especially simplified workpiece machining during production. Costs can also be kept low.

[0029] Furthermore, it is proposed that the sealing contour of the valve tappet assembly be designed to form a flat seat. This advantageously allows for a high degree of sealing of the flat seat with good controllability / control quality through linearized characteristic curves. Moreover, a particularly simple and cost-effective design of the sealing element of the valve tappet assembly, and thus also of the valve tappet assembly itself, can be achieved. The valve tappet assembly preferably has the sealing element at its axial end, which forms the flat sealing seat. The sealing element is, in particular, flat and planar, at least on one side facing the nozzle / valve seat.

[0030] Alternatively, if the sealing contour of the valve tappet unit is designed to form a sealing seat other than a flat seat, such as a conical seat, a ball seat, a lens seat, a saddle seat, etc., a significant linearization of the characteristic curves can advantageously be achieved even with such types of sealing seats.

[0031] If the valve tappet assembly is at least substantially cylindrical, a high degree of characteristic linearity can be advantageously achieved. In particular, this can advantageously prevent flow separation or suction effects on a surface of the valve tappet assembly, which can vary in intensity depending on the stroke and thus lead to undesirable variations in flow force profiles at different strokes. At least one end-edge region of the valve tappet assembly facing the nozzle assembly could be designed to be at least substantially, preferably within the limits of standard manufacturing tolerances, free of chamfers, significant radii, and / or steps.

[0032] Furthermore, it is proposed that the valve tappet unit comprises a base body and the sealing element forming the sealing contour, which is mounted to the base body. The base body forms an end-edge region of the valve tappet unit facing the nozzle assembly. An axial end edge of the valve tappet unit, arranged in this end-edge region, together with the flow optimization unit of the nozzle assembly, forms a control gap for adjusting the flow force of a valve incorporating the valve tappet unit. This allows for particularly advantageous flow guidance. Advantageously, characteristic curve linearization can be achieved. Advantageously, good controllability and / or high control accuracy can be achieved. The minimum distance of the base body (i.e., the valve tappet unit outside the sealing element) is located between the end edge and the side wall of the conical recess.The sealing element is preferably located even closer to the nozzle assembly, particularly to the valve seat, than the end edge of the conical recess and therefore regulates the flow rate. In particular, the flow rate profile remains unaffected by the conical recess / control gap at different strokes, since the opening cross-section between the valve tappet assembly and the conical recess always remains larger than the opening cross-section between the sealing element of the valve tappet assembly and the valve seat / flow channel opening. However, the control gap preferably influences the (pressure-supporting) flow force of the valve. By initially selecting the shape of the conical recess, especially the initial conical angle, the flow force of the valve / pressure drop within the valve can advantageously be adjusted / set.In particular, the conical recess ensures that the flow force / pressure drops less sharply / more slowly / in a more controlled manner when the sealing element forming the flat sealing seat of the valve tappet assembly lifts off the valve seat than would be the case without the conical recess. Specifically, the base body of the valve tappet assembly is free from contact with the nozzle assembly in all operating states of the valve tappet assembly, including when the valve is closed. In particular, the control gap has a finite minimum size.

[0033] Furthermore, a pressure and / or flow control valve, in particular a pressure-opening proportional pressure and / or flow control valve for gases, is proposed, comprising a magnetic armature and a valve housing in which the magnetic armature is axially movable, wherein the valve assembly is mounted and / or integrated into the valve housing. This allows valves with advantageous flow-stroke and force-stroke characteristics to be obtained, particularly regardless of the design and / or valve seat type of the valve stem assembly. Advantageously, a high degree of tightness can be achieved while simultaneously maintaining good, and in particular linear, controllability. The magnetic armature is, in particular, part of an electromagnet of the pressure and / or flow control valve. The magnetic armature is, in particular, connected to, or at least operatively connected to, the valve stem assembly. The magnetic armature could also form, at least partially and / or almost completely, the valve stem assembly.

[0034] Furthermore, a method for operating the pressure and / or flow control valve is proposed, wherein at least one flow-current characteristic of the pressure and / or flow control valve is linearized by means of the valve device. This allows valves with advantageous characteristic curves to be obtained.

[0035] The valve device, pressure and / or flow control valve, and / or method according to the invention are not limited to the application and embodiment described above. In particular, the valve device, pressure and / or flow control valve, and / or method according to the invention may, to achieve a functionality described herein, comprise a different number of individual elements, components, and units than that specified herein. Drawings

[0036] Further advantages become apparent from the following description of the drawings. The drawings illustrate four exemplary embodiments of the invention. The drawings, the description, and the claims contain numerous features in combination. A person skilled in the art will expediently consider the features individually and combine them into meaningful further combinations.

[0037] They show: Fig. 1. A schematic cross-sectional view of part of a valve with a valve device. Fig. 2a a schematic flowchart of a procedure for operating the valve, Fig. 2b schematically illustrates a relationship relevant to the procedure between different characteristic curves of the valve, Fig. 3 a schematic cross-sectional view of part of a valve with a first alternative valve device, Fig. 4 a schematic cross-sectional view of part of a valve with a second alternative valve device and Fig. 5 a schematic cross-sectional view of part of a valve with a third alternative valve device. Description of the exemplary implementations

[0038] The Fig. Figure 1 schematically shows a cross-sectional view of part of a valve 26a. The valve 26a forms a pressure and / or flow control valve. The valve 26a is designed as a pressure-opening proportional pressure and / or flow control valve for gases, in particular for hydrogen-containing gas mixtures and / or for hydrogen gas. The valve 26a includes an electromagnet (not shown, as it is known from the prior art). The valve 26a has a valve housing 78a. The valve housing 78a externally defines the valve 26a, and in particular a flow chamber of the valve 26a. The valve housing 78a serves to accommodate the components of the valve 26a and / or the electromagnet. The valve 26a, in particular the electromagnet of the valve 26a, has a magnetic armature 76a. The magnetic armature 76a is movably arranged in the valve housing 78a. The magnetic armature 76a is movable in the axial direction 36a.The magnetic armature 76a forms the exemplary embodiment of the . Fig. 1 also includes a valve tappet unit 18a. The valve 26a has a valve device 80a. The valve device 80a is integrated into the valve housing 78a. The valve device 80a is mounted in the valve housing 78a.

[0039] The valve assembly 80a comprises the valve tappet unit 18a. The valve tappet unit 18a is cylindrical. The valve assembly 80a includes a nozzle assembly 10a. The nozzle assembly 10a comprises a nozzle. The nozzle assembly 10a includes a flow channel 12a for the gases. The flow channel 12a includes an inner flow channel opening 14a. The flow channel opening 14a is formed by the nozzle assembly 10a. The flow channel opening 14a is located on the side of the flow channel 12a facing the valve tappet unit 18a. The nozzle assembly 10a forms a valve seat 16a. The valve seat 16a completely surrounds the flow channel opening 14a. The valve seat 16a is designed to accommodate the valve tappet unit 18a. The valve tappet unit 18a has a sealing element 68a. The sealing element 68a is arranged at an axial end 20a of the valve tappet unit 18a, which faces the nozzle assembly 10a.The sealing element 68a forms a sealing contour. The sealing contour is closed all around. The sealing contour is designed to selectively close and open the flow channel 12a gas-tight (hydrogen gas-tight) on the valve seat 16a. The sealing contour of the valve tappet unit 18a is designed to form a flat seat, in particular a flat sealing seat.

[0040] The sealing element 68a has a flat, planar surface on one side facing the nozzle assembly 10a. The sealing element 68a is free of a sealing cone or the like. The valve tappet assembly 18a has a base body 66a. The sealing element 68a is mounted in the base body 66a. The sealing element 68a is approximately flush with the base body 66a on one side facing the nozzle assembly 10a. The sealing element 68a extends only over a portion of the total end surface of the axial end 20a of the valve tappet assembly 18a.

[0041] The nozzle assembly 10a includes a geometric flow optimization unit 22a. The geometric flow optimization unit 22a is designed to linearize the valve characteristics of the valve 26a. Specifically, it is designed to linearize a flow-force characteristic and / or a flow-current characteristic of the valve 26a, which includes the valve tappet assembly 18a (with the flat sealing seat). The geometric flow optimization unit 22a is located in a region of the nozzle assembly 10a that is radially (in radial direction 54a) outside the valve seat 16a and facing the valve tappet assembly 18a. The flow optimization unit 22a has a flow-shaping geometry 24a. The flow channel 12a and the flow shaping geometry 24a are each formed by separate / each by other component components 82a, 84a.The two component parts 82a and 84a of the nozzle assembly 10a are mounted together. The first component part 82a of the nozzle assembly 10a forms the flow channel 12a. The first component part 82a of the nozzle assembly 10a forms the valve seat 16a. In the . Fig. In the embodiment shown in Figure 1, the first component 82a of the nozzle assembly 10a is formed in one piece / monolithically with the valve housing 78a. The second component 84a of the nozzle assembly 10a forms the flow-shaping geometry 24a. In the Fig. In the embodiment shown in Figure 1, the second component 84a of the nozzle assembly 10a is designed separately from the valve housing 78a. In this case, the second component 84a of the nozzle assembly 10a is mounted inside the valve housing 78a.

[0042] The flow-shaping geometry 24a is designed as a conical recess 30a. The conical recess 30a is centered around a central axis 28a of the flow channel 12a. The conical recess 30a tapers towards a closing direction 32a of the valve tappet unit 18a. The closing direction 32a runs parallel to the central axis 28a from the valve tappet unit 18a towards the nozzle assembly 10a. The valve tappet unit 18a is partially immersed in the conical recess 30a, at least in one operating state where the valve tappet unit 18a is seated on the valve seat 16a. The conical recess 30a has side walls 34a. The side walls 34a of the conical recess 30a are free of curvature in the axial direction 36a of the conical recess 30a. The side walls 34a of the conical recess 30a have a conical angle 38a with respect to the axial direction 36a. The conical angle 38a lies between 10° and 80°, preferably between 20° and 70°, and more preferably between 30° and 60°. In the Fig. In the example shown, the cone angle 38a is approximately 45°. The side walls 34a of the cone recess 30a form a slope region 40a of the cone recess 30a. The entire slope region 40a of the cone recess 30a lies radially (in the radial direction 54a) further outwards (further from the central axis 28a) than the axial end 20a of the valve tappet unit 18a. The base body 66a of the valve tappet unit 18a forms an end edge region 70a of the valve tappet unit 18a facing the nozzle assembly 10a. An axial end edge 72a of the valve tappet unit 18a, arranged in the end edge region 70a of the valve tappet unit 18a, together with the geometric flow optimization unit 22a of the nozzle assembly 10a, in particular with the flow shaping geometry 24a, preferably with the side wall 34a of the cone recess 30a, forms a control gap 74a for adjusting the flow force of the valve 26a comprising the valve tappet unit 18a.The cone recess 30a has a cone length of 90a. The cone recess 30a has a cone diameter of 92a. The control gap 74a, the cone diameter 92a, the cone length 90a, and / or the cone angle 38a are each adjustable to set specific requirements for changing the flow force, in particular the flow-stroke and force-stroke characteristics. The control gap 74a serves to adjust / control the force / pressure drop of the valve 26a. A gap between the sealing element 68a and the valve seat 16a serves to adjust / control the flow through the valve 26a.

[0043] The geometric flow optimization unit 22a has a first additional flow-shaping geometry 42a. The first additional flow-shaping geometry 42a differs from a cone geometry. The first additional flow-shaping geometry 42a is formed and arranged separately from the flow-shaping geometry 24a. The first additional flow-shaping geometry 42a is arranged radially between the flow channel opening 14a and the flow-shaping geometry 24a. The first additional flow-shaping geometry 42a is formed as a flow edge 46a. The flow edge 46a forms a flow separation edge 58a for a gas flow flowing out of the flow channel opening 14a in the direction of the flow-shaping geometry 24a. The first further flow shaping geometry 42a is formed as part of the first component 82a of the nozzle assembly 10a.Alternatively, the first further flow shaping geometry 42a could also be designed as part of the second component 84a of the nozzle assembly 10a.

[0044] The geometric flow optimization unit 22a has a second flow-shaping geometry 44a. The second flow-shaping geometry 44a differs from a cone geometry. The second flow-shaping geometry 44a is formed and arranged separately from the flow-shaping geometry 24a. The second flow-shaping geometry 44a is formed and arranged separately from the first flow-shaping geometry 42a. The second flow-shaping geometry 44a is arranged radially between the flow channel opening 14a and the flow-shaping geometry 24a. The second flow-shaping geometry 44a is arranged radially between the first flow-shaping geometry 42a and the flow-shaping geometry 24a. The second further flow-shaping geometry 44a is designed as a further flow edge 48a.The further flow edge 48a forms a guide edge 60a for a gas flow flowing radially (in radial direction 54a) into the flow-shaping geometry 24a. The second further flow-shaping geometry 44a is formed as part of the second component 84a of the nozzle assembly 10a.

[0045] The geometric flow optimization unit 22a has a third additional flow shaping geometry 50a. The third additional flow shaping geometry 50a differs from a cone geometry. The third additional flow shaping geometry 50a is formed and arranged separately from the flow shaping geometry 24a. The third additional flow shaping geometry 50a is formed and arranged separately from the first additional flow shaping geometry 42a. The third additional flow shaping geometry 50a is formed and arranged separately from the second additional flow shaping geometry 44a. The third additional flow shaping geometry 50a is arranged radially (in the radial direction 54a) further outwards than the flow shaping geometry 24a. The third additional flow shaping geometry 50a is the radially outermost of all flow shaping geometries 24a, 42a, 44a, 50a of the geometric flow optimization unit 22a.All flow-shaping geometries 24a, 42a, 44a, 50a create a flow channel and guide it through geometric boundaries / walls. The third additional flow-shaping geometry 50a is designed as an axial flow deflection 52a. The axial flow deflection 52a is intended to generate a flow direction for the gas flow exiting the geometric flow optimization unit 22a after passing through all flow-shaping geometries 24a, 42a, 44a, 50a of the geometric flow optimization unit 22a, which runs at least substantially parallel to the axial direction 36a of the valve tappet unit 18a. Alternatively, the flow direction of the gas flow leaving the geometric flow optimization unit 22a after passing all flow shaping geometries 24a, 42a, 44a, 50a of the geometric flow optimization unit 22a could also have a finite angle to the axial direction 36a of the valve tappet unit 18a.This finite angle would then be significantly smaller than the cone angle 38a of the cone recess 30a. The third further flow-shaping geometry 50a is formed as part of the second component 84a of the nozzle assembly 10a.

[0046] In summary, the geometric flow optimization unit 22a, extending along the radial direction 54a in the flow direction from inside to outside, comprises the following sequence of flow-shaping geometries 24a, 42a, 44a, 50a: i) the flow separation edge 58a, ii) a horizontally planar flow region 56a, iii) the guide edge 60a, iv) the conical recess 30a, and v) the axial flow deflection 52a. Following the axial flow deflection 52a, the gas flow exits the valve 26a through a gas outlet 86a of the valve 26a, specifically of the valve housing 78a. Before exiting the flow channel 12a, the gas flow enters the flow channel 12a through a gas inlet 88a of the valve 26a, specifically of the valve housing 78a.

[0047] The Fig. Figure 2a shows a schematic flow diagram of a procedure for operating the valve 26a. In at least one procedure step 94a, at least the flow-current characteristic and / or at least the flow-force characteristic of the valve 26a is linearized by means of the valve device 80a. Fig. Figure 2b schematically shows the relationship between the flow (mass flow)-force characteristic curve of valve 26a (right), which is to be linearized, and the mass flow-stroke characteristic curve of valve 26a (left) and the force-stroke characteristic curve of valve 26a (center). Matched nonlinear mass flow-stroke and force (flow force)-stroke characteristic curves yield the linearized relationship between flow / mass flow (ṁ) and force / flow force (F) relevant for the operating behavior of valve 26a. The stroke is denoted by the abbreviation s.

[0048] In the Fig. Figures 3 to 5 show three further embodiments of the invention. The following descriptions and drawings are essentially limited to the differences between the embodiments, whereby, with regard to identically designated components, particularly those with the same reference numerals, reference is also generally made to the drawings and / or the description of the other embodiments, especially those of the Fig. 1 and Fig. 2, reference can be made. To distinguish the embodiments, the letter a is the reference numeral of the embodiment in the Fig. 1 and Fig. 2. In the exemplary embodiments of the Fig. In letters 3 to 5, the letter a is replaced by the letters b to d.

[0049] The Fig. Figure 3 schematically shows a cross-sectional view of a section of the Fig. 1 corresponding part of a valve 26b with a first alternative valve device 80b. The first alternative valve device 80b has a nozzle assembly 10b with a geometric flow optimization unit 22b comprising a flow-shaping geometry 24b. The flow-shaping geometry 24b is designed as a conical recess 30b. A part of a side wall 34b of the conical recess 30b is curved in the axial direction 36b of the conical recess 30b. In the Fig. In the example shown, the curvature 96b of a side wall 34b of the conical recess 30b is concave. Alternatively, the curvature 96b could also be convex.

[0050] The Fig. Figure 4 schematically shows a cross-sectional view of a section of the Fig. 1 corresponding part of a valve 26c with a second alternative valve device 80c. The second alternative valve device 80c has a nozzle assembly 10c which forms a flow channel 12c and a valve seat 16c surrounding a flow channel opening 14c of the flow channel 12c. The second alternative valve device 80c has a valve tappet unit 18c which has a sealing element 68c with a circumferential sealing contour at an axial end 20c. The sealing contour is designed to selectively seal the flow channel 12c gas-tight on the valve seat 16c. The sealing contour of the valve tappet unit 18c is designed to form a sealing seat other than a flat seat. In the Fig. In the embodiment shown in Figure 4, the sealing element 68c forms a conical seat 64c. Alternatively, the sealing element 68c could also form a ball seat, a lens seat, or a saddle seat.

[0051] The Fig. Figure 5 schematically shows a cross-sectional view of a section of the Fig.1 corresponding part of a valve 26d with a third alternative valve device 80d. The third alternative valve device 80d has a nozzle assembly 10d. The nozzle assembly 10d has a monolithic component 62d. The nozzle assembly 10d is configured as the monolithic component 62d. The monolithic component 62d has at least one flow channel 12d of the nozzle assembly 10d and a flow-shaping geometry 24d (a conical recess 30d) of a geometric flow-optimizing unit 22d of the nozzle assembly 10d. In addition, the monolithic component 62d has the entire remainder of the geometric flow-optimizing unit 22d.The monolithic component 62d has a flow separation edge 58d of the geometric flow optimization unit 22d, a horizontally planar flow region 56d of the geometric flow optimization unit 22d, a guide edge 60d of the geometric flow optimization unit 22d, and an axial flow deflection 52d of the geometric flow optimization unit 22d. The monolithic component 62d is also formed in one piece with a part of a valve housing 78d of the valve 26d. Reference sign 10 nozzle assembly 12 Flow channel 14 Flow channel opening 16 Valve seat 18 Valve tappet unit 20 Axial end 22 Geometric Flow Optimization Unit 24 Flow shaping geometry 26 valve 28 Central axis 30 Conical recess 32 Closing direction 34 side wall 36 Axial direction 38 cone angles 40 gradient range 42 Further flow shaping geometry 44 Further flow shaping geometry 46 Flow edge 48 Flow edge 50 More Flow Shaping Geometry 52 Axial flow deflection 54 Radial direction 56 Horizontal flat flow area 58 Flow separation edge 60 Leading edge 62 Monolithic component 64 Conical seat 66 Basic shapes 68 Sealing element 70 End edge area 72 Axial end edge 74 Tax column 76 magnetic armatures 78 Valve housings 80 Valve device 82 Component 84 Component 86 Gas outlet 88 Gas intake 90 cone length 92 cone diameter 94 Procedure step 96 Curvature

Claims

[1] Valve device (80a-d), in particular pressure and / or flow control valve device, preferably for hydrogen gas and / or hydrogen-containing gas mixtures, comprising a nozzle assembly (10a-d) which forms at least one flow channel (12a-d) and a valve seat (16a-d) surrounding a flow channel opening (14a-d) of the flow channel (12a-d), and comprising a valve tappet unit (18a-d) which forms a sealing contour, preferably circumferential, at an axial end (20a-d) which is provided for a selectively gas-tight, in particular hydrogen gas-tight, sealing contact on the valve seat (16a-d), characterized by , that the nozzle assembly (10a-d) has at least in a region radially outside the valve seat (16a-d) and facing the valve tappet assembly (18a-d) a geometric flow optimization unit (22a-d) with at least one flow shaping geometry (24a-d). [2] Valve device (80a-d) according to claim 1, characterized by , that the geometric flow optimization unit (22a-d) is provided at least for a linearization of at least one valve characteristic curve, in particular a flow-current characteristic curve and / or a flow-force characteristic curve of a valve (26a-d) having the valve tappet unit (18a-d). [3] Valve device (80a-d) according to claim 1 or 2, characterized by , that the flow shaping geometry (24a-d) is designed as a conical recess (30a-d) centered in particular around a central axis (28a-d) of the flow channel (12a-d), which preferably tapers in the closing direction (32a-d) of the valve tappet unit (18a-d). [4] Valve device (80a-d) according to claim 3, characterized bythat the valve tappet unit (18a-d) is partially immersed in the cone recess (30a-d) at least in one operating condition sitting on the valve seat (16a-d), preferably in all regular operating conditions. [5] Valve device (80a; 80c-d) according to claim 3 or 4, characterized by , that at least a large part of a side wall (34a; 34c-d) of the cone recess (30a; 30c-d) is free of curvature in the axial direction (36a; 36c-d) of the cone recess (30a; 30c-d). [6] Valve device (80a; 80c-d) according to any one of claims 3 to 5, characterized by , that at least a large part of a side wall (34a; 34c-d) of the cone recess (30a; 30c-d) has a cone angle (38a; 38c-d) between 10° and 80°, preferably between 20° and 70° and preferably between 30° and 60°. [7] Valve device (80a; 80c-d) according to any one of claims 3 to 6, characterized by, that an entire slope area (40a; 40c-d) of the cone recess (30a; 30c-d) is radially further outward than the axial end (20a; 20c-d) of the valve tappet unit (18a; 18c-d). [8] Valve device (80b) according to claim 3 or 4, characterized by , that at least part of a side wall (34b) of the cone recess (30b) is concavely or convexly curved in the axial direction (36b) of the cone recess (30b). [9] Valve device (80a-d) according to any one of the preceding claims, characterized by , that the geometric flow optimization unit (22a-d) has a further flow shaping geometry (42a-d, 44a-d, 50a-d) or several further flow shaping geometries (42a-d, 44a-d, 50a-d) which is / are different from a cone geometry. [10] Valve device (80a-d) according to claim 9, characterized by, that the further flow shaping geometry (42a-d, 44a-d) or at least one of the several further flow shaping geometries (42a-d, 44a-d) is arranged radially between the flow channel opening (14a-d) and the flow shaping geometry (24a-d). [11] Valve device (80a-d) according to claim 9 or 10, characterized by , that the further flow shaping geometry (42a-d, 44a-d) or at least one of the several further flow shaping geometries (42a-d, 44a-d) is formed as a flow edge (46a-d, 48a-d). [12] Valve device (80a-d) according to claim 11, characterized by , that the flow edge (46a-d, 48a-d) or at least one of the flow edges (46a-d, 48a-d) forms a flow separation edge (58a-d) for a gas flow flowing out of the flow channel opening (14a-d) in the direction of the flow shaping geometry (24a-d). [13] Valve device (80a-d) according to claim 11 or 12, characterized by, that the flow edge (46a-d, 48a-d) or at least one of the flow edges (46a-d, 48a-d) forms a guiding edge (60a-d) for a gas flow radially into the flow-shaping geometry (24a-d). [14] Valve device (80a-d) according to claim 9, characterized by , that the further flow shaping geometry (50a-d) or at least one of the several further flow shaping geometries (50a-d) is arranged radially further outwards than the flow shaping geometry (24a-d). [15] Valve device (80a-d) according to claim 14, characterized by , that the further flow shaping geometry (50a-d) or at least one of the several further flow shaping geometries (50a-d) is designed as an axial flow deflection (52a-d). [16] Valve device (80a-d) according to claims 6 and 15, characterized by, that the axial flow deflection (52a-d) is intended to generate a flow direction of a gas flow leaving the geometric flow optimization unit (22a-d) after passing through all flow shaping geometries (24a-d, 42a-d, 44a-d, 50a-d) of the geometric flow optimization unit (22a-d), the angle of which to an axial direction (36a-d) of the valve tappet unit (18a-d) is significantly smaller than the cone angle (38a-d) or which runs at least substantially parallel to the axial direction (36a-d) of the valve tappet unit (18a-d). [17] Valve device (80a-d) at least according to claims 3, 11, 13 and 15, characterized by , that the geometric flow optimization unit (22a-d) in radial direction (54a-d) from inside to outside, in particular in flow direction, comprises the following sequence of flow shaping geometries (24a-d, 42a-d, 44a-d, 50a-d): i) the flow separation edge (58a-d), ii) a horizontally planar flow area (56a-d), iii) the leading edge (60a-d), iv) the cone recess (30a-d) and v) the axial flow deflection (52a-d). [18] Valve device (80d) according to any of the preceding claims, characterized by , that the nozzle assembly (10d) has a monolithic component (62d) which simultaneously forms the flow channel (12d) and the flow shaping geometry (24d) of the geometric flow optimization unit (22d), preferably the entire geometric flow optimization unit (22d). [19] Valve device (80a-c) according to any one of claims 1 to 17, characterized by , that the flow channel (12a-c) and the flow shaping geometry (24a-c) are each formed by separate, adjoining component parts (82a-c, 84a-c) of the nozzle assembly (10a-c). [20] Valve device (80a-d) according to any one of the preceding claims, characterized by, that the sealing contour of the valve tappet unit (18a-d) is designed to form a flat seat, in particular a flat sealing seat. [21] Valve device (80c) according to any one of claims 1 to 19, characterized by , that the sealing contour of the valve tappet unit (18c) is designed to form a sealing seat other than a flat seat, such as a conical seat (64c), a ball seat, a lens seat, a saddle seat, etc. [22] Valve device (80a-d) according to any one of the preceding claims, characterized by , that the valve tappet unit (18a-d) is at least substantially cylindrical. [23] Valve device (80a-d) according to any of the preceding claims, characterized by, that the valve tappet unit (18a-d) comprises a base body (66a-d) and a sealing element (68a-d) forming the sealing contour, which is mounted on the base body (66a-d), wherein the base body (66a-d) forms an end edge region (70a-d) of the valve tappet unit (18a-d) facing the nozzle assembly (10a-d), and wherein an axial end edge (72a-d) of the valve tappet unit (18a-d) arranged in the end edge region (70a-d) together with the geometric flow optimization unit (22a-d) of the nozzle assembly (10a-d) forms a control gap (74a-d) for adjusting a flow force of a valve (26a-d) comprising the valve tappet unit (18a-d). [24] Pressure and / or flow control valve, in particular a pressure-opening proportional pressure and / or flow control valve for gases, with a magnetic armature (76a-d) and with a valve body (78a-d) within which the magnetic armature (76a-d) is arranged to be axially movable, characterized by, that a valve device (80a-d) according to one of the preceding claims is mounted and / or integrated into the valve housing (78a-d). [25] Method for operating a pressure and / or flow control valve according to claim 24, characterized by , that at least one flow-current characteristic of the pressure and / or quantity control valve is linearized by means of the valve device (80a-d).

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